EP3019749B1 - Verstellpumpe und getriebesteuerung - Google Patents

Verstellpumpe und getriebesteuerung Download PDF

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Publication number
EP3019749B1
EP3019749B1 EP14736358.4A EP14736358A EP3019749B1 EP 3019749 B1 EP3019749 B1 EP 3019749B1 EP 14736358 A EP14736358 A EP 14736358A EP 3019749 B1 EP3019749 B1 EP 3019749B1
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EP
European Patent Office
Prior art keywords
control
pressure
primary
pump
gearbox
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Active
Application number
EP14736358.4A
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German (de)
English (en)
French (fr)
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EP3019749A2 (de
Inventor
Ludger Holtmann
Thilo MAUSER
Van Doan Nguyen
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Magna Powertrain Bad Homburg GmbH
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Magna Powertrain Bad Homburg GmbH
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Publication of EP3019749A2 publication Critical patent/EP3019749A2/de
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    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16H—GEARING
    • F16H61/00—Control functions within control units of change-speed- or reversing-gearings for conveying rotary motion ; Control of exclusively fluid gearing, friction gearing, gearings with endless flexible members or other particular types of gearing
    • F16H61/02—Control functions within control units of change-speed- or reversing-gearings for conveying rotary motion ; Control of exclusively fluid gearing, friction gearing, gearings with endless flexible members or other particular types of gearing characterised by the signals used
    • F16H61/0262—Control functions within control units of change-speed- or reversing-gearings for conveying rotary motion ; Control of exclusively fluid gearing, friction gearing, gearings with endless flexible members or other particular types of gearing characterised by the signals used the signals being hydraulic
    • F16H61/0265—Control functions within control units of change-speed- or reversing-gearings for conveying rotary motion ; Control of exclusively fluid gearing, friction gearing, gearings with endless flexible members or other particular types of gearing characterised by the signals used the signals being hydraulic for gearshift control, e.g. control functions for performing shifting or generation of shift signals
    • F16H61/0267—Layout of hydraulic control circuits, e.g. arrangement of valves
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04C—ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT PUMPS
    • F04C14/00—Control of, monitoring of, or safety arrangements for, machines, pumps or pumping installations
    • F04C14/18—Control of, monitoring of, or safety arrangements for, machines, pumps or pumping installations characterised by varying the volume of the working chamber
    • F04C14/22—Control of, monitoring of, or safety arrangements for, machines, pumps or pumping installations characterised by varying the volume of the working chamber by changing the eccentricity between cooperating members
    • F04C14/223—Control of, monitoring of, or safety arrangements for, machines, pumps or pumping installations characterised by varying the volume of the working chamber by changing the eccentricity between cooperating members using a movable cam
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04C—ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT PUMPS
    • F04C14/00—Control of, monitoring of, or safety arrangements for, machines, pumps or pumping installations
    • F04C14/18—Control of, monitoring of, or safety arrangements for, machines, pumps or pumping installations characterised by varying the volume of the working chamber
    • F04C14/22—Control of, monitoring of, or safety arrangements for, machines, pumps or pumping installations characterised by varying the volume of the working chamber by changing the eccentricity between cooperating members
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04C—ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT PUMPS
    • F04C14/00—Control of, monitoring of, or safety arrangements for, machines, pumps or pumping installations
    • F04C14/24—Control of, monitoring of, or safety arrangements for, machines, pumps or pumping installations characterised by using valves controlling pressure or flow rate, e.g. discharge valves or unloading valves
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04C—ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT PUMPS
    • F04C14/00—Control of, monitoring of, or safety arrangements for, machines, pumps or pumping installations
    • F04C14/28—Safety arrangements; Monitoring
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16H—GEARING
    • F16H57/00—General details of gearing
    • F16H57/04—Features relating to lubrication or cooling or heating
    • F16H57/0434—Features relating to lubrication or cooling or heating relating to lubrication supply, e.g. pumps ; Pressure control
    • F16H57/0446—Features relating to lubrication or cooling or heating relating to lubrication supply, e.g. pumps ; Pressure control the supply forming part of the transmission control unit, e.g. for automatic transmissions
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16H—GEARING
    • F16H61/00—Control functions within control units of change-speed- or reversing-gearings for conveying rotary motion ; Control of exclusively fluid gearing, friction gearing, gearings with endless flexible members or other particular types of gearing
    • F16H61/0021—Generation or control of line pressure
    • F16H61/0025—Supply of control fluid; Pumps therefore
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04C—ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT PUMPS
    • F04C2240/00—Components
    • F04C2240/80—Other components
    • F04C2240/81—Sensor, e.g. electronic sensor for control or monitoring
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04C—ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT PUMPS
    • F04C2270/00—Control; Monitoring or safety arrangements
    • F04C2270/02—Power
    • F04C2270/025—Controlled or regulated
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16H—GEARING
    • F16H61/00—Control functions within control units of change-speed- or reversing-gearings for conveying rotary motion ; Control of exclusively fluid gearing, friction gearing, gearings with endless flexible members or other particular types of gearing
    • F16H61/0021—Generation or control of line pressure
    • F16H2061/0037—Generation or control of line pressure characterised by controlled fluid supply to lubrication circuits of the gearing

Definitions

  • the invention relates to a variable displacement pump for hydraulic transmission controls, in particular vane pump, with variable displacement and with a pump regulator for drain pressure control, wherein the outlet pressure of the pump in a compensation chamber and adjustable by the pump regulator control pressure in a control pressure chamber acts on an adjustable cam ring, wherein the pressure in the control pressure chamber and an additional spring force the cam in the direction of maximum swiveling, d. H.
  • a transmission control for automatic transmission which, inter alia, has a primary hydraulic circuit for the force transmission-relevant elements of the transmission and a primary pressure control valve which opens when reaching or exceeding the adjustable primary pressure bypass to a secondary hydraulic circuit and further exceeding the primary pressure has additional pressure limiting function for the primary pressure, and wherein the secondary hydraulic circuit of the cooling and lubrication of the transmission is used.
  • variable displacement pumps for hydraulic transmission controls for automatic transmission are from the WO2012149931 A1 known.
  • control circuits in which initially only the primary pressure control valve is effective and opens from the set primary pressure, the connection to the secondary hydraulic circuit and then acting in the secondary hydraulic circuit pressure on the pump controller is effective, so then the pump control in the direction of a advocatesschwenkenden or abregelnden pump is adjusted, ie the delivery volume is smaller.
  • control circuits with a variable displacement pump and an automatic transmission are known in which a separate control pressure from a control circuit simultaneously to the pump controller of the variable, the primary pressure control valve and optionally a pressure reducing valve in the secondary or lubrication circuit is effective.
  • a separate control pressure from a control circuit simultaneously to the pump controller of the variable, the primary pressure control valve and optionally a pressure reducing valve in the secondary or lubrication circuit is effective.
  • variable displacement pump for hydraulic transmission controls in particular vane pump with variable displacement and with a pump regulator for drain pressure control, in which the outlet pressure of the pump in a compensation chamber and adjustable by the pump regulator control pressure in a control pressure chamber acts on an adjustable cam , wherein the pressure in the control pressure chamber and an additional spring force the cam in the direction of maximum swiveling, ie adjusted maximum displacement, and with a transmission control for automatic transmission, which, inter alia, has a primary hydraulic circuit for the force transmission-relevant elements of the transmission and a primary pressure control valve which opens when reaching or exceeding the adjustable primary pressure bypass to a secondary hydraulic circuit and further exceeding the primary pressure an additional Pressure relief function for the primary pressure, and wherein the secondary hydraulic circuit of the cooling and lubrication of the transmission is used,
  • control loops or control circuits of the pump control and the transmission (primary pressure) control are separated from each other and thus independently switched individually or interconnected.
  • a further variable displacement pump and transmission control is characterized in that a sensing pressure chamber of the primary pressure control valve for the primary pressure relative to the primary hydraulic circuit via the inflow of Fsseldrucchunt or via the outflow of the sensing pressure chamber can be switched on or off by the switching valve ( FIG. 2 and 3 ).
  • variable displacement pump and transmission control is preferred in which by the switching valve of the Sekundärhydrauliknikzul or the secondary hydraulic circuit connection from the primary pressure control valve or can be switched off ( FIG. 4 ).
  • variable displacement pump and transmission control is preferred in which the inflow or the connection to the pump regulator or to the control pressure chamber from the primary pressure circuit or primary hydraulic circuit can be switched on or off by the switching valve ( FIG. 5 ).
  • Another variable displacement pump and transmission control is characterized in that the inflow of the sensing pressure chamber of the primary pressure control valve from the primary hydraulic circuit through the valve is switched on and off and the outflow of the sensing pressure chamber via a hydraulic resistance z.
  • variable displacement pump and transmission control is preferred in which the outflow of the sensing pressure chamber to the tank or oil sump through the valve is switched on and off and the inflow to the pressure sensing chamber from the primary hydraulic circuit via a hydraulic resistance, eg. B. a throttle takes place.
  • a hydraulic resistance eg. B. a throttle takes place.
  • a variable displacement pump and transmission control is preferred in which a control pressure of a control pressure circuit of the transmission control acts on an area of the control pressure chamber of the pump regulator (large area, spring space, aufregelnd) and on the switching valve (spring chamber area) closing ( Figure 2 , Switching valve switches inflow of the sensing pressure chamber).
  • control pressure of the transmission control acts on a surface of the control pressure chamber of the pump controller (large area, spring chamber, aufregelnd) and on the spring chamber of the switching valve opening ( Figure 3 , Outflow of the sensing pressure chamber of the primary pressure control valve).
  • variable displacement pump and transmission control is preferred in which the control pressure of the transmission control acts on a surface of the control pressure chamber of the pump regulator (large area, spring space, aufregelnd) and on the spring chamber of the switching valve opening ( Figure 4 , Switching valve switches inflow to the secondary hydraulic circuit).
  • a variable displacement pump and transmission control is characterized in that a control pressure of the transmission control acts on a surface of the control pressure chamber of the pump controller (large area, spring space, aufregelnd) and on the spring chamber of the primary pressure valve, and the secondary pressure opening on the switching valve acts ( Figure 5 ; Switching valve regulates inflow from primary hydraulic circuit to the pump regulator; Pump control regulates with primary pressure).
  • FIG. 1 an adjustable vane pump 1 with variable displacement and a transmission control for automatic transmission.
  • the vane pump 1 with variable displacement has a displaceable cam ring 3, which is shown with respect to a rotor 5 in its maximum deflected position.
  • radially displaceable wings 7 are arranged in radial slots.
  • the pressure acts in a so-called compensation chamber 9 in the direction of pivoting back of the cam ring 3 up to a zero promotion of the pump on the opposite side acts on the displaceable cam ring 3, the pressure in a so-called control pressure chamber 11 to a pressure acting surface, the is greater than the pressure acting surface of the compensation chamber, wherein the cam ring 3 additionally acts in the direction of the swinging 3, ie in the direction of the maximum displacement of the vane pump 1 by a spring 13.
  • the spring 13 also acts after switching off the pump and the transmission in the direction of maximum deflection of the cam ring 3, to allow immediate supply of oil and a start of the transmission at the start of the motor vehicle.
  • the compensation chamber 9 is acted upon via a control oil line 15 shown in dashed lines with the line 17 at the pump outlet, that is to say with the maximum pressure that can be generated by the pump.
  • the crizdruccsch 11 of the adjustable vane pump 1 is connected via a control oil line 19 with a control valve 21, also called pump regulator, wherein the pump regulator the control pressure in the control pressure chamber 11 and in the feed line 19 between a pressure from the pump outlet to the line 17, which is supplied via the line 23 to the control valve 21, and a tank pressure in a tank line 25 varies.
  • the control valve 21 or the pump regulator has a control piston 27, which on one side with a spring 29 and the pressure in a chamber, weleher acts on a small pressure acting surface 31 of the control piston 27 and which is connected via a control line 33 to the Pumpenauslass Kunststoff Geb, acts in an opening direction, so that the control piston 27, the control pressure chamber 11 initially unthrottled with the Pumpenauslasstik in the line 17 connects, while the connection of the control pressure chamber 11 shuts off via the control piston 27 to the tank drain with the tank line 25.
  • the flow rate of the pump from the pump outlet of the conduit 17 leads to a primary hydraulic circuit 39 of the transmission, which supplies all force-relevant elements such as hydraulically shiftable clutches, brake bands, synchronizing devices for gears or adjustable conical disks and pressure cylinder, for example for CVT transmission.
  • the primary hydraulic circuit 39 is first supplied with the pump volume flow via the pump outlet line 17 until a corresponding primary pressure, which is needed to actuate the aforementioned transmission elements, has built up in the primary hydraulic circuit 39.
  • a primary pressure control valve 41 remains closed until this operating point.
  • the primary pressure control valve 41 has a hydraulic pressure chamber 43 with a control surface, on which via a control line 47, the primary pressure can act.
  • the primary pressure control valve has a hydraulic control surface 45, on which the pressure in the control circuit 49 can act, and a spring 51, which acts together with the pressure in the control circuit 49 in the closing direction of the primary pressure control valve 41. If, in the primary hydraulic circuit 39, the corresponding primary pressure in the pressure chamber 43 of the primary pressure control valve is exceeded so far that it can open the primary pressure control valve 41 relative to the pressure in the control circuit 49 and the spring force 51, then a bypass volume flow flows through the line 53 to a so-called secondary hydraulic circuit 55. which is used for cooling and lubrication of the corresponding transmission components.
  • the pressure that builds up in this line 55 in the secondary hydraulic circuit 55, thereby also on the pump controller 21 via the line 37 is effective and causes that with sufficient volume flow demand and the corresponding, caused by pressure buildups in the primary and secondary hydraulic circuit of the pump controller a lower control pressure as the pressure at the pump outlet 17 in the control pressure chamber 13 adjusts, so that the variable displacement pump 1 swings back according to the only maximum volume flow requirement.
  • the pressure in the control circuit 49 additionally acts on an additional pressure acting surface 59 of a pressure reducing valve 63, via which, after reaching the pressure set there for a lubricating hydraulic circuit 61, a bypass volumetric flow to this separate lubricating hydraulic circuit 61 is throttled accordingly.
  • the pressure set at the pressure reducing valve 63 is thus changed by the control circuit pressure.
  • the circuit shown here has the (disadvantageous) function that first the primary hydraulic circuit 39 must perform the required pressure buildup and then only the primary pressure control valve 41 opens the line to the secondary hydraulic circuit 55, so that only then a corresponding control pressure acts on the pump controller 21 and the pump 1 can pivot back accordingly to the maximum required volume flow, which can be quickly exceeded, for example, at high speed of the pump 1.
  • the pump control itself is therefore firstly with a certain time delay and secondly changed by a possibly then opposite control movement of the primary pressure control valve 41 in turn in its control variable and possibly disturbed. This can lead to high time delays and possibly to instabilities of the control in different operating points.
  • variable displacement pump 1 with its compensation chamber 9, its control pressure chamber 11 and the additional spring 19 therein and the corresponding lines 15 and 17 correspond to the illustration in FIG Figure 1.1 and should not be mentioned here again to avoid repetition.
  • the pump regulator 70 itself here has a different structure and is therefore provided with the reference numeral 70.
  • a control pressure chamber 72 in which also a corresponding adjusting spring 74 sets the basic position of the control piston 76, is connected to a control pressure line 78 to the control circuit 49 and thus to the pressure prevailing in the control circuit 49.
  • the control circuit 49 with its pressure acts as in Figure 1.1 again on the surface 45 of the primary pressure control valve 41, on which on the other side of the primary pressure control valve piston of the Pressure in the primary hydraulic circuit 39 acts, as already in Figure 1.1 described. Furthermore, the pressure from the control circuit 49 also acts on the pressure reducing valve 63 of the lubricating hydraulic circuit 61.
  • the primary pressure control valve 41 which should open when the primary pressure is reached
  • the pump regulator 70 which also at Reaching the primary pressure
  • the stroke volume of the pump 1 should pivot back, should essentially intervene simultaneously and thus can influence each other to instability.
  • control circuit pressure in the control circuit 49 additionally acts in addition to the lubricant circuit pressure on the pressure reducing valve 63, so that again a change and possible disruption of the control circuit pressure can occur through additionally connected consumers.
  • On the pump regulator 70 acts on a small annular surface 80 of the pump outlet pressure from the pump outlet 17, which upon reaching a set on the pump controller 70 maximum pressure, which is set by the spring 74 and the control pressure in the control pressure chamber 72, a control edge of the pump controller 70 to the tank outlet 82nd opens and thus an intermediate pressure between the pump outlet pressure and the tank pressure in the pump control chamber 11 is adjusted.
  • FIG. 2 an inventive arrangement of a variable displacement pump is shown with a transmission control.
  • An adjustable vane pump 100 which here compared to the previous one Figures 1.1 and 1.2 is shown with the opposite direction of rotation, has an outlet 102, via which a compensation chamber 104 can be acted upon by the pump outlet pressure and thereby adjust the cam 105 of the variable vane pump 100 according to the zero position.
  • a pressure from the pump controller 110 via a control pressure line 112 in the control pressure chamber 106 in Vietnamesestende direction as well as the Aufregelfeder 108.
  • the control valve or the pump regulator 110 is shown in its structure something different than in the previous figures.
  • the pump regulator 110 is connected to the control circuit 49 of the automatic transmission with its large piston surface 114 in the pressure chamber, in which also the spring 116 acting on the control piston 120 is arranged.
  • the pump outlet pressure ie the maximum pressure prevailing in the system, acts from the outlet line 102 of the vane pump 100.
  • the control pressure chamber 106 of the pump is in the in FIG. 2 represented position of the control piston 120 of the pump controller 110 via the control line 122, via the first control edge 124 and the control pressure line 112 downstream of the pump controller 110 connected to the pump outlet pressure in the line 102 and thus fully regulated the pump.
  • the tank 128 is in the case of an automatic transmission, for example, the oil sump at the bottom of the automatic transmission.
  • the primary hydraulic circuit 130 of the automatic transmission is shown here as a flat rate as a hydraulic resistance consumer.
  • a bypass line 132 leads from the primary hydraulic circuit to a primary pressure control valve 134.
  • the primary pressure control valve 134 is able to conduct a bypass volume flow from the line 132 into the secondary hydraulic circuit 136, which is also represented symbolically here by a hydraulic resistance as a consumer, given a set pressure.
  • the secondary hydraulic circuit 136 and the lubrication circuit are simplified to a single hydraulic circuit without the interposition of a pressure reducing valve shown.
  • a (inventive) switching valve 138 is arranged in the hydraulic circuit to turn off the primary pressure control valve 134 in its function or switch on.
  • the switching valve 138 is arranged between supply lines 140 and 142, which can obstruct or open it accordingly, wherein the feed line 142 leads into a pressure sensing chamber 144 of the primary pressure control valve 134. If the switching valve 138 is switched to its open position, which is done for example by lowering the control pressure in the control pressure circuit 49, which acts on a piston surface of the switching valve 138 in a control pressure chamber 148, which also includes a corresponding spring 150, against an annular surface 146, on which the supply line 142, the primary circuit pressure is effective, the piston of the valve 138 opens the connection between the lines 140 and 142 and allows an inflow from the primary pressure circuit into the pressure sensing chamber 144 and thus a pressure build-up in the sensing pressure chamber 144, since the outflow from the pressure sensing chamber 144 into a tank 154 or the oil sump of the automatic transmission is limited by a hydraulic resistance 152, for example in the form of a throttle.
  • a hydraulic resistance 152 for example in the form of a
  • the primary pressure control valve 134 may open a control edge 156 to the secondary hydraulic circuit 136 and direct a corresponding bypass flow from the primary hydraulic circuit 130 and the high pressure line 102 to the secondary hydraulic circuit 136, which then also to a secondary pressure buildup in the secondary hydraulic circuit 136 and thus to an effective secondary pressure force on the piston surface 158 in Pressure chamber with the spring 160 of the primary pressure valve 134 is effective.
  • the separately switchable valve 138 makes it possible to initially disable the primary pressure control valve 134, so that until the setting of the primary pressure only the pump controller 110 of the variable displacement pump 1 is effective with its control loop.
  • FIG. 3 is both the vane pump 100 with its pressure chambers and the pump controller 110 and the primary pressure control valve 134 and the primary hydraulic circuit 130, the secondary hydraulic circuit 136 and the control circuit 49 as in FIG. 2 arranged and interconnected, so that the same reference numerals and the same functional description applies to these areas except for the other arrangement of a switching valve 170.
  • the switching valve 170 is in the FIG. 3 connected between the sensing pressure chamber 144 of the primary pressure control valve 134 and the tank 154 and the oil sump of the transmission.
  • the switching valve 170 is in this case by a Spring 172 initially open in the pressureless state, so that from the primary hydraulic circuit 130 and the high-pressure line 102, an outflow via a control line 174 from this high-pressure or primary pressure region via a hydraulic resistance 176, for example in the form of a throttle, to the sensing pressure chamber 144. Since the connection in the drain 178 to the tank 154 is opened by the switching valve 170, no substantial pressure can build up in the sensing pressure chamber 144, which can initiate or trigger the function of the primary pressure control valve 134.
  • FIG. 4 is a further inventive arrangement of a variable displacement pump with a transmission control shown.
  • the vane pump 100 with its pump controller 110 and the basic arrangement of the primary pressure control valve 134, the primary hydraulic circuit 130 and the secondary hydraulic circuit 136 identical to those FIG. 2 and 3 .
  • the Fsseler pressure chamber 180 of the primary pressure control valve has no outflow, so that the primary pressure in the primary hydraulic circuit 130 and in the high-pressure line 102 directly via an inflow from the Primärhydrauliknik 130 and attenuated only by a damping throttle 182 or by inflow and can be effective without outflow.
  • a switching valve 184 is connected in this diagram between the outlet 186 of the primary pressure control valve 134 to the secondary hydraulic circuit 136. This means that after reaching the primary pressure set at the primary pressure control valve 134, the primary pressure control valve 134 also remains inoperative, as long as the valve 184 is closed, since after opening the control edge 188, the primary pressure in the closed circuit to the secondary circuit 136 through the valve 184 186 also in the pressure chamber 190th With the spring of the primary pressure valve 134 is effective and thus the primary pressure control valve 134 brings the control edge 188 back toward the closed position.
  • FIG. 5 a further embodiment of a variable displacement pump according to the invention is shown with a transmission control, which differs principally in that here not a primary pressure control valve 212 is set when starting the transmission hydraulics out of action, but a controller 204 of the vane pump 100.
  • the primary pressure control valve 212 thus forms the controller for the control circuit, which assumes its first control position, and then via a switching valve 200 in addition the pump controller 204 and thus the adjustment of the vane pump 100 are turned on.
  • the connection that is, the circuit of the vane pump 100 itself to the pump controller 204 and also the piston or control edge structure of the pump controller 204 remain as before in the Figures 2 . 3 and 4 described.
  • the inflow via the line 202 to the pump regulator 204 via the switching valve 200 which thus can open the flow from the high-pressure line 102 and the primary hydraulic circuit 130 and shut off.
  • the control pressure from the control circuit 49 acts as in the Figures 2 . 3 and 4 on the large piston surface 206 of the pump controller 204 in the spring chamber of the pump controller 204, but in FIG. 5 unlike in the Figures 2 . 3 and 4
  • the pressure sensing chamber 214 has only one inflow from the primary pressure circuit 130 via a corresponding damping throttle 216.
  • the secondary hydraulic circuit 218 is separated in this circuit via a pressure reducing valve 224 from the lubricating hydraulic circuit 220.
  • the prioritization of the amount of oil in the transmission generally has the first function to prevent a shortage of supply of the primary hydraulic circuit. All transmission-relevant elements in the transmission are supplied via this primary hydraulic circuit.
  • the secondary hydraulic circuit supplies the cooling and lubrication in the transmission, ie subordinate functions.
  • An object of the invention is thus to close the secondary hydraulic circuit at low flow rates of the pump.
  • the solution of the problem is thus in the limitation of the consumers upstream control valve types, in particular the upstream of the consumers valves for prioritizing the amount of oil, and the separation of the two functions of pressure control and prioritization.
  • the solution representing circuits are, for example, in the FIGS. 2 to 5 shown.
  • Prioritization in these embodiments means that first the primary hydraulic circuit amount, then the secondary hydraulic circuit amount, and then the final volume flow amount of the variable displacement pump should be adjusted.
  • the aim of the invention is to separate the crizdorfnbeaufschlagung for the variable displacement and for the transmission hydraulics as a consumer from each other.
  • the primary pressure control valves in the FIGS. 2 to 5 following functions.
  • the primary pressure control valves are initially set to their control function by the pending primary pressure and open a control edge to the secondary hydraulic circuit when a primary pressure level is exceeded.
  • Vane pump 59th Pressure acting area Third lifting ring 61st Lubricating hydraulic circuit 5th rotor 63rd Pressure reducing valve 7th wing 70th pump regulator 9th compensation chamber 72nd Control pressure chamber 11th Control pressure chamber 74th adjusting spring 13th feather 76th control piston 15th Control oil line 78th Control pressure line 17th management 80th ring surface 19th Control oil line 82nd tank drain 21st control valve 100th Vane pump 23rd management 102nd outlet pipe 25th tank line 104th compensation chamber 27th control piston 105th lifting ring 29th feather 106th Control pressure chamber 31st Pressure acting area 108th Aufregelfeder 33rd control line 110th pump regulator 35th Pressure acting area 112th Regulating pressure line 37th Control pressure line 114th piston area 39th Primary hydraulic circuit 116th feather 41st Primary pressure control valve 118th ring surface 43rd pressure chamber 120th control piston 45th control surface 122nd control line 47th control line 124th control edge 49th control circuit 126th control edge 51st feather 1

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  • Engineering & Computer Science (AREA)
  • General Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • Physics & Mathematics (AREA)
  • Fluid Mechanics (AREA)
  • Details And Applications Of Rotary Liquid Pumps (AREA)
  • Control Of Transmission Device (AREA)
  • Rotary Pumps (AREA)
  • Control Of Positive-Displacement Pumps (AREA)
EP14736358.4A 2013-07-08 2014-07-01 Verstellpumpe und getriebesteuerung Active EP3019749B1 (de)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
DE102013107180 2013-07-08
PCT/EP2014/064002 WO2015003960A2 (de) 2013-07-08 2014-07-01 Verstellpumpe und getriebesteuerung

Publications (2)

Publication Number Publication Date
EP3019749A2 EP3019749A2 (de) 2016-05-18
EP3019749B1 true EP3019749B1 (de) 2019-04-17

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EP14736358.4A Active EP3019749B1 (de) 2013-07-08 2014-07-01 Verstellpumpe und getriebesteuerung

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US (1) US10060524B2 (es)
EP (1) EP3019749B1 (es)
JP (1) JP2016530432A (es)
CN (1) CN105308321B (es)
CA (1) CA2914748A1 (es)
MX (1) MX2015016888A (es)
WO (1) WO2015003960A2 (es)

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DE102016215228A1 (de) * 2016-08-16 2018-02-22 Zf Friedrichshafen Ag Verfahren zum Betätigen eines Hydrauliksystems eines Getriebes mit einer verstellbaren Hydraulikpumpe
JP6485477B2 (ja) * 2017-03-16 2019-03-20 マツダ株式会社 可変容量オイルポンプを備えた自動変速機の油圧制御装置
DE102017112700A1 (de) * 2017-06-08 2018-12-13 Schwäbische Hüttenwerke Automotive GmbH Steuerventil
DE102018214330A1 (de) * 2018-08-24 2020-02-27 Zf Friedrichshafen Ag Pumpeneinrichtung für Hydrauliksystem zur Fahrzeuggetriebeschaltung

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DE19652420A1 (de) * 1996-12-09 1998-06-10 Luk Fahrzeug Hydraulik Stromregelanordnung für eine hydraulische Fördereinrichtung
WO1998028179A1 (en) * 1996-12-24 1998-07-02 Itt Automotive Electrical Systems, Inc. Hydraulically powered fan and power steering in a vehicle
US5875630A (en) * 1997-06-10 1999-03-02 Sauer Inc. Hydraulic drive assembly
FR2826408A1 (fr) * 2001-06-22 2002-12-27 Mannesmann Rexroth Sa Procede et dispositif de repartition d'un flux d'entree ent re un flux de sortie prioritaire et un flux de sortie second aire
JP4674740B2 (ja) * 2001-07-24 2011-04-20 株式会社不二越 可変容量形ベーンポンプ
DE10247669B4 (de) * 2001-10-29 2011-05-19 Ixetic Bad Homburg Gmbh Ventilanordnung
US8529221B2 (en) * 2003-10-03 2013-09-10 Honeywell International Inc. Method and system for fuel control in a gas turbine engine
DE102006039698B3 (de) * 2006-08-21 2007-10-25 Joma-Hydromechanic Gmbh Förderpumpe
US8182238B2 (en) * 2009-04-03 2012-05-22 Ford Global Technologies, Llc Variable displacement transmission pump control
DE112012001968A5 (de) * 2011-05-04 2014-01-23 Ixetic Bad Homburg Gmbh Verstellpumpe

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US20160116059A1 (en) 2016-04-28
CA2914748A1 (en) 2015-01-15
CN105308321A (zh) 2016-02-03
US10060524B2 (en) 2018-08-28
MX2015016888A (es) 2016-04-11
WO2015003960A2 (de) 2015-01-15
WO2015003960A3 (de) 2015-06-04
JP2016530432A (ja) 2016-09-29
CN105308321B (zh) 2018-01-09
EP3019749A2 (de) 2016-05-18

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